Leading-edge steering assembly

ABSTRACT

A leading-edge steering system is provided for a front suspension of an off-road vehicle. The leading-edge steering system is comprised of a spindle assembly that supports a drive axle assembly to conduct torque from a transaxle to a front wheel. A first rod-end joint pivotally couples an upper suspension arm and the spindle assembly, and a second rod-end joint pivotally couples a lower suspension arm and the spindle assembly. A steering rod-end joint pivotally couples a first end of a steering rod with a leading-edge portion of the spindle assembly. A steering gear is coupled with a second end of the steering rod and configured to move the steering rod, such that the spindle assembly rotates with respect to the upper and lower suspension arms. The leading-edge portion is configured to exert primarily tensile forces on the steering rod during travel over rough terrain.

PRIORITY

This application claims the benefit of and priority to U.S. Provisional Application, entitled “Off-Road Front Suspension System,” filed on Apr. 3, 2017 and having application Ser. No. 62/480,960.

FIELD

The field of the present disclosure generally relates to vehicle suspension systems. More particularly, the field of the invention relates to an off-road front suspension system configured to improve the mechanical strength and performance of off-road drivetrains.

BACKGROUND

A double wishbone suspension is a well-known independent suspension design using upper and lower wishbone-shaped arms to operably couple a front wheel of a vehicle. Typically, the upper and lower wishbones or suspension arms each has two mounting points to a chassis of the vehicle and one mounting joint at a spindle assembly or knuckle. A shock absorber and a coil spring may be mounted onto the wishbone to control vertical movement of the front wheel. The double wishbone suspension facilitates control of wheel motion throughout suspension travel, including controlling such parameters as camber angle, caster angle, toe pattern, roll center height, scrub radius, scrub, and the like.

Double wishbone suspensions may be used in a wide variety of vehicles, including heavy-duty vehicles, as well as many off-road vehicles, as shown in FIG. 1. FIG. 1 shows an off-road vehicle 100 that is of a Side by Side variety. The Side by Side is a four-wheel drive off-road vehicle that typically seats between two and six occupants, and is sometimes referred to as a Utility Task Vehicle (UTV), a Recreational Off-Highway Vehicle (ROV), or a Multipurpose Off-Highway Utility Vehicle (MOHUV). In addition to the side-by-side seating arrangement, many UTVs have seat belts and roll-over protection, and some may have a cargo box at the rear of the vehicle. A majority of UTVs come factory equipped with hard tops, windshields, and cab enclosures.

The double-wishbone suspension often is referred to as “double A-arms”, although the arms may be A-shaped, L-shaped, J-shaped, or even a single bar linkage. In some embodiments, the upper arm may be shorter than the lower arm so as to induce negative camber as the suspension jounces (rises). Preferably, during turning of the vehicle, body roll imparts positive camber gain to the lightly loaded inside wheel, while the heavily loaded outer wheel gains negative camber.

The spindle assembly, or knuckle, is coupled between the outboard ends of the upper and lower suspension arms. In some designs, the knuckle contains a kingpin that facilitates horizontal radial movement of the wheel, and rubber or trunnion bushings for vertical hinged movement of the wheel. In some relatively newer designs, a ball joint may be disposed at each outboard end to allow for vertical and radial movement of the wheel. A bearing hub, or a spindle to which wheel bearings may be mounted, may be coupled with the center of the knuckle.

Constant velocity (CV) joints allow pivoting of the suspension arms and the spindle assembly, while a drive shaft coupled to the CV joint delivers power to the wheels. Although CV joints are typically used in front wheel drive vehicles, off-road vehicles such as four-wheeled buggies comprise CV joints at all wheels. Constant velocity joints typically are protected by a rubber boot and filled with molybdenum disulfide grease.

Given that off-road vehicles routinely travel over very rough terrain, such as mountainous regions, there is a desire to improve the mechanical strength and performance of off-road drivetrain and suspension systems, while at the same reducing the mechanical complexity of such systems.

SUMMARY

A leading-edge steering system is provided for a front suspension of an off-road vehicle. The leading-edge steering system is comprised of a spindle assembly configured to support a drive axle assembly to conduct torque from a transaxle to a front wheel. A first rod-end joint is configured to pivotally couple an upper suspension arm and the spindle assembly, and a second rod-end joint is configured to pivotally couple a lower suspension arm and the spindle assembly. A steering rod-end joint pivotally couples a first end of a steering rod with a leading-edge portion of the spindle assembly. The steering rod-end joint may be either a Heim joint or a bushing joint. A steering gear is disposed in a chassis of the off-road vehicle and coupled with a second end of the steering rod. The steering gear is configured to move the steering rod with respect to the spindle assembly, such that moving the steering rod rotates the spindle assembly with respect to the upper suspension arm and the lower suspension arm. The leading-edge portion is configured to exert primarily tensile forces on the steering rod during traveling of the front wheel over rough terrain.

In an exemplary embodiment, a leading-edge steering system for a front suspension of an off-road vehicle comprises a spindle assembly configured to support a drive axle assembly to conduct torque from a transaxle to a front wheel; a first rod-end joint configured to pivotally couple an upper suspension arm and the spindle assembly; a second rod-end joint configured to pivotally couple a lower suspension arm and the spindle assembly; a steering rod-end joint configured to pivotally couple a first end of a steering rod with a leading-edge portion of the spindle assembly; and a steering gear disposed in a chassis of the off-road vehicle and coupled with a second end of the steering rod.

In another exemplary embodiment, the leading-edge portion of the spindle assembly is comprised of two parallel prongs extending forward with respect to the drive axle, the parallel prongs being configured to fixedly receive a bolt that hingedly receives the steering rod-end joint, such that moving the steering rod rotates the spindle assembly with respect to the upper suspension arm and the lower suspension arm. In another exemplary embodiment, the steering rod-end joint is comprised of a bushing that couples the steering rod with the spindle assembly, such that moving the steering rod rotates the spindle assembly with respect to the upper suspension arm and the lower suspension arm. In another exemplary embodiment, the bushing is configured to hingedly couple the steering rod with a bolt that is fastened through two parallel prongs extending forwardly from the spindle assembly. In another exemplary embodiment, the bushing is configured to facilitate horizontal rotation of the spindle assembly with respect to the upper suspension arm and the lower suspension arm during vertical motion of the spindle assembly during operation of the off-road vehicle.

In another exemplary embodiment, the steering rod-end joint is comprised of a ball that is rotatable within a casing that is threadably coupled with the steering rod, such that moving the steering rod rotates the spindle assembly with respect to the upper suspension arm and the lower suspension arm. In another exemplary embodiment, the ball is configured to be fastened by way of a bolt between a pair of parallel prong extending forwardly from the spindle assembly, such that moving the steering rod rotates the spindle assembly horizontally with respect to the upper suspension arm and the lower suspension arm during vertical motion of the spindle assembly due to operation of the off-road vehicle. In another exemplary embodiment, the steering rod-end joint is coupled with the spindle assembly forward of the drive axle so as to advantageously decrease leverage of the front wheel on the steering rod and substantially eliminate bump steer that may occur due to traveling over rough terrain.

In another exemplary embodiment, the steering gear is configured to move the steering rod rightward during clockwise turning of the steering gear, and wherein the steering gear is configured to move the steering rod leftward during counterclockwise turning of the steering gear. In another exemplary embodiment, the leading-edge portion is configured to rotate the spindle assembly rightward during clockwise turning of the steering gear, and wherein the leading-edge portion is configured to rotate the spindle assembly leftward during counterclockwise turning of the steering gear. In another exemplary embodiment, the leading-edge portion is configured to exert primarily tensile forces on the steering rod during traveling of the front wheel over rough terrain. In another exemplary embodiment, the leading-edge portion is configured to substantially eliminate bump steer that may occur due to forces exerted on the front wheel by the rough terrain.

BRIEF DESCRIPTION OF THE DRAWINGS

The drawings refer to embodiments of the present disclosure in which:

FIG. 1 illustrates an exemplary embodiment of an off-road vehicle that is particularly suitable for implementation of an off-road front suspension system in accordance with the present disclosure;

FIG. 2 illustrates a front view of a front suspension system that is configured to couple a front wheel with a passenger side of an off-road vehicle;

FIG. 3 illustrates a front view of an exemplary embodiment of outboard rod-end joints coupling a spindle assembly with upper and lower suspension arms;

FIG. 3A illustrates a lower isometric view of an exemplary embodiment of a leading-edge steering system that may be incorporated into the front suspension of the off-road vehicle;

FIG. 3B illustrates a front plan view of the leading-edge steering system of FIG. 3A;

FIG. 4A illustrates a front plan view of an exemplary embodiment of rod-end joint coupling a spindle assembly with a suspension arm;

FIG. 4B illustrates a side plan view of the rod-end joint of FIG. 4A; and

FIG. 5 illustrates a perspective view of an exemplary embodiment of rod-end joint that includes a lubricating race and a lubrication fitting.

While the present disclosure is subject to various modifications and alternative forms, specific embodiments thereof have been shown by way of example in the drawings and will herein be described in detail. The invention should be understood to not be limited to the particular forms disclosed, but on the contrary, the intention is to cover all modifications, equivalents, and alternatives falling within the spirit and scope of the present disclosure.

DETAILED DESCRIPTION

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present disclosure. It will be apparent, however, to one of ordinary skill in the art that the invention disclosed herein may be practiced without these specific details. In other instances, specific numeric references such as “first joint,” may be made. However, the specific numeric reference should not be interpreted as a literal sequential order but rather interpreted that the “first joint” is different than a “second joint.” Thus, the specific details set forth are merely exemplary. The specific details may be varied from and still be contemplated to be within the spirit and scope of the present disclosure. The term “coupled” is defined as meaning connected either directly to the component or indirectly to the component through another component. Further, as used herein, the terms “about,” “approximately,” or “substantially” for any numerical values or ranges indicate a suitable dimensional tolerance that allows the part or collection of components to function for its intended purpose as described herein.

In general, the present disclosure describes a suspension for coupling a front wheel with a chassis of an off-road vehicle. The suspension comprises an upper suspension arm that includes two inboard mounting points to the chassis and one outboard rod-end joint to a spindle assembly coupled with the front wheel. A lower suspension arm comprises two inboard mounting points to the chassis and one outboard rod-end joint to the spindle assembly. Each outboard rod-end joint is comprised of a ball that is rotatable within a casing that is threadably coupled with each of the upper and lower suspension arms. A bolt fastens each of the balls between a pair of parallel prongs extending from the spindle assembly, such that the upper and lower suspension arms may pivot with respect to the spindle assembly during vertical motion of the spindle assembly, as well as during horizontal rotation of the spindle assembly due to steering. A strut comprising a shock absorber and a coil spring is coupled between the lower suspension arm and the chassis. The upper suspension arm is configured to facilitate coupling the strut between the lower suspension arm and the chassis. A steering rod is coupled with the spindle assembly by way of a steering rod-end joint that is disposed at a front of the spindle assembly. The steering rod-end joint is comprised of a ball that is rotatable within a casing that is threadably coupled with the steering rod. A pair of parallel prongs and a bolt hingedly couple the steering rod-end with the spindle assembly, such that the steering rod-end joint allows vertical and horizontal rotational motion of the spindle assembly during operation of the off-road vehicle. The steering rod-end joint is coupled with the spindle assembly forward of a drive axle, thereby decreasing leverage of the front wheel on the steering rod and substantially eliminating bump steer that may occur due to rough terrain.

FIG. 1 shows an off-road vehicle 100 that is particularly suitable for implementation of an off-road front suspension system in accordance with the present disclosure. As disclosed hereinabove, the off-road vehicle 100 generally is of a Utility Task Vehicle (UTV) variety that seats two occupants, includes a roll-over protection system 104, and may have a cab enclosure 108. Rear wheels 112 of the off-road vehicle 100 may be operably coupled with a chassis 116 by way of a trailing arm suspension system. Front wheels 120 may be operably coupled with the chassis 116 by way of the front suspension system disclosed herein. It should be understood, however, that the front suspension system of the present disclosure is not to be limited to the off-road vehicle 100, but rather the front suspension system may be incorporated into a wide variety of off-road vehicles, other than UTVs, without limitation.

FIG. 2 illustrates a front view of a front suspension system 124 that is configured to couple the front wheel 120 with a passenger side of the off-road vehicle 100. The front suspension system 124 is comprised of an upper suspension arm 128 and a lower suspension arm 132 that couple the front wheel 120 with the chassis 116. Each of the upper and lower suspension arms 128, 132 comprises two inboard mounting points 136 to the chassis 116 and one outboard mounting joint to a spindle assembly 140. As will be recognized, the upper and lower suspension arms 128, 132 generally are of a double wishbone variety of suspension that facilitates controlling various parameters affecting the orientation of the wheel 120 with respect to the off-road vehicle 100, such as, by way of non-limiting example, camber angle, caster angle, toe pattern, roll center height, scrub radius, and scuff.

It should be understood that although the front suspension system 124 is disclosed specifically in connection with the passenger side of the off-road vehicle 100, a driver side front suspension system is to be coupled with a driver side of the off-road vehicle. It should be further understood that the driver side front suspension system is substantially identical to the front suspension system 124, with the exception that the driver side front suspension system is configured specifically to operate with the driver side of the off-road vehicle 100. As will be appreciated, therefore, the driver side front suspension system and the front suspension system 124 may be configured as reflections of one another across a longitudinal midline of the off-road vehicle 100.

As shown in FIG. 2, a strut 144 that is comprised of a shock absorber and a coil spring is mounted to the lower suspension arm 132 by way of a lower pivot 148. An upper pivot (not shown) couples a top of the strut 144 to the chassis 116. The strut 144 is configured to control vertical motion of the front suspension system 124 due to movement of the front wheel 120 as the off-road vehicle 100 travels over bumpy terrain. The upper suspension arm 128 may be suitably configured, such as in the form of a J-arm, so as to facilitate coupling the strut 144 between the lower suspension arm 132 and the chassis 116 in lieu of being coupled between the upper suspension arm and the chassis.

In some embodiments, coupling the strut 144 with the lower suspension arm 132 positions the strut at between 8 inches and 10 inches lower, with respect to the chassis 116, than the position of the strut when coupled with the upper suspension arm 128. Experimental observation has shown that the lower position of the strut 144 generally facilitates a lower center of gravity of the off-road vehicle 100 and a relatively smaller shock angle, as well as eliminating a need for extending the strut towers through and above a hood of the off-road vehicle 100. In one embodiment, the coupling of the strut 144 with the lower suspension arm 132 positions the strut at substantially 90-degrees with respect to the lower pivot 148 and the upper pivot during full compression of the strut.

As shown in FIG. 2, a drive axle 146 is coupled between a transaxle and the front wheel 120. The drive axle 146 is configured to conduct torque from the transaxle to the front wheel 120 and accommodate vertical pivoting motion of the front suspension assembly 124 in response to road conditions. As best shown in FIG. 3, the drive axle 146 is comprised of a constant velocity (CV) joint 152 that is coupled with the spindle assembly 140 onto which the front week is mounted. The CV joint 152 allows uninterrupted torque transmission from the transaxle to the front wheel 120 during vertical pivoting of the front suspension assembly 124 due to road conditions. As will be appreciated, the spindle assembly 140 generally supports the CV joint 152 and the front wheel 120 by way of one or more roller bearings (not shown).

As further shown in FIG. 3, the spindle assembly 140 is pivotally coupled with the upper and lower suspension arms 128, 132. An upper rod-end joint 156 couples the upper suspension arm 128 to the spindle assembly 140, and a lower rod-end joint 160 couples the lower suspension arm 132 to the spindle assembly. Preferably, the upper and lower rod-end joints 156, 160 are of a Heim joint variety, wherein each of the joints is comprised of a ball 164 that is movable within a casing 168 that is threadably coupled with each of the suspension arms 128, 132. A bolt 172 fastens each of the balls 164 between a pair of parallel prongs 176 extending from the spindle assembly 140. It is contemplated that a recess 180 disposed between each pair of parallel prongs 176 has a shape and a size that are suitable to fixedly receive the ball 164 and allow for a desired degree of movement of the casing 168 on the ball. Thus, during vertical motion of the spindle assembly 140, as well as during horizontal rotation of the spindle assembly 140 due to steering, the balls 164 rotate within their respective casings 168, allowing the upper and lower suspension arms 128, 132 to pivot with respect to the spindle assembly 140.

Upon inspection of FIG. 3, it will be recognized that the upper and lower rod-end joints 156, 160 are similar to Clevis fasteners. For example, each pair of parallel prongs 176 is similar to a Clevis, the bolt 172 is similar to a Clevis pin, and the ball 164 and casing 168 are similar to a tang. As such, each of the upper and lower rod-end points 156, 160 provides two shear planes that may withstand twice the incident force that may be withstood by single shear joints that are used in conventional front suspensions.

In the embodiment illustrated in FIG. 3, a steering rod 184 couples the spindle assembly 140 with a steering system of the off-road vehicle 100. The steering rod 184 is coupled with the spindle assembly 140 by way of a rod-end joint 188 that is similar to the upper and lower rod-end joints 156, 160. It is contemplated, therefore, that the rod-end joint 188 may be of the Heim-joint variety or may be of a bushing variety, as desired. A pair of parallel prongs 192 and a bolt 196 hingedly couple the steering rod 184 with the spindle assembly 140. As will be appreciated, the rod-end joint 188 allows vertical and horizontal rotational motion of the spindle assembly 140 during operation of the off-road vehicle 100.

In the embodiment illustrated in FIG. 3, the rod-end joint 188 is coupled with the spindle assembly 140 forward of the drive axle 146, thereby providing a leading-edge steering system to the off-road vehicle 100. Experimentation has demonstrated that the leading-edge steering system shown in FIG. 3 advantageously decreases leverage of the front wheel 120 on the rod-end joint 188 and the steering rod 184, thereby substantially eliminating bump steer that may occur due to forces exerted on the front wheel by rough terrain.

FIGS. 3A-3B illustrate an exemplary embodiment of a leading-edge steering system 240 that is advantageously incorporated into the front suspension of the off-road vehicle 100. Similar to the embodiment illustrated in FIG. 3, the leading-edge steering system 240 is comprised of a steering rod 184 that is coupled with the spindle assembly 140 by way of a rod-end joint 188 that is disposed forward of the drive axle 146. As disclosed above, the rod-end joint 188 may be of the Heim-joint variety or may be of a bushing variety, such that the rod-end joint 188 allows vertical and horizontal rotational motion of the spindle assembly 140. Opposite of the rod-end joint 188, the steering rod 184 is coupled with a steering gear 244 that is mounted onto a central location of the chassis 116. During operating the off-road vehicle, turning the steering gear 244 clockwise moves the steering rod 184 toward the spindle assembly 140, causing the front wheel 120 to turn rightward. Turning the steering gear 244 moves the steering rod 184 away from the spindle assembly 140, thereby turning the front wheel 120 leftward.

During traveling over rough terrain, the steering rods 184 comprising the leading-edge steering system 240 are exposed primarily to tensile forces, unlike tie-rods comprising conventional trailing-edge steering systems that endure primarily compression forces. It will be recognized by those skilled in the art that although the yield strength of steel generally is independent of tension and compression, the steering rod 184 generally may support a greater load in tension than in compression. As will be appreciated, a tensile force requires all sections of the steering rod 184 to yield before failure of the steering rod may occur, whereas in the case of a compression force, failure of the steering rod 184 due to buckling generally requires a relatively lower force acting at a weakest section of the rod. Under the action of the compression force, therefore, failure of the steering rod 184 may occur when any one section of the steel fails rather than requiring all sections to fail as occurs with tensile forces. As such, the leading-edge steering system 240 is capable of withstanding relatively much greater forces due to rough terrain than may be tolerated by conventional, trailing-edge steering systems.

FIGS. 4A-4B illustrate an exemplary embodiment of a rod-end 200 that may be pivotally coupled with either of the upper and lower suspension arms 128, 132 of the spindle assembly 140, as described herein. Like the rod-end joints 156, 160, the rod-end 200 is generally of the Heim-joint variety. The rod-end 200 is comprised of a ball 204 that is retained within a casing 208, such that the ball 204 may be rotated within the casing 208. A threaded shank 212, or a weld-in tube end, is fixedly coupled with the casing 208 so as to enable coupling the rod-end to one of the suspension arms 128, 132. The threaded shank 212 may be fixedly coupled with the suspension arm by way of a lock-nut 214 (see FIG. 5) that may be threaded onto the shank 212 and rotated into forcible contact with the suspension arm. It is contemplated that the threaded shank 212 may be configured with left-hand threads or right-hand threads, without limitation.

A bore 216 extends through the ball 204 and is configured to receive the bolt 172. The bore 216 and the bolt 172 facilitate mounting the rod-end 200 to the spindle assembly 140. In particular, the bolt 172 may be passed through suitable threaded holes in the prongs 176 and through the bore 216 so as to fixate the ball 204 in the recess 180. With the ball 204 fixated between the parallel prongs 176, the casing 208 and the suspension arm to which the rod-end 200 is fastened may be freely moved with respect to the spindle assembly 140.

As best shown in FIG. 4B, a misalignment spacer 220 may be disposed on each of opposite sides of the ball 204. The misalignment spacers 220 ensure that the ball 204 remains centered within the recess 180, between the parallel prongs 176, while providing a relatively high degree of clearance for rotation of the casing 208 on the ball 204. In some embodiments, the misalignment spacers 220 may be threaded or press-fitted into suitable countersunk holes in the ball 204. In some embodiments, the ball 204 and the misalignment spacers 220 may be machined as a single component comprising an extended ball that may be installed into the casing 208 during manufacturing of the rod-end 200.

In some embodiments, a lubricating race may be incorporated into the rod-end as to ensure sufficient lubrication is available to the ball and casing during operation of the rod-end. For example, in an exemplary embodiment of a rod-end 224, illustrated in FIG. 5, a lubricating race 228 is disposed between the ball 204 and an interior of the casing 208. In some embodiments, the lubricating race 228 may be comprised of a heavy duty, injection molded Teflon impregnated Nylon race that is configured to ensure smooth and precise movement of the ball 204 within the casing 208. In some embodiments, the lubricating race 228 may be comprised of a thin chamber between the ball 204 and an interior of the casing 208. A suitable lubricant, such as a high-quality grease, may be disposed within the thin chamber so as to lubricate movement between the ball 204 and the casing 208. A lubrication fitting 232 may be disposed in the casing 208 and in fluid communication with the thin camber to facilitate periodic replenishment of the lubricant within the thin chamber.

In some embodiments, the rod-ends 200, 224 may be configured to have self-lubricating properties. For example, in some embodiments, the balls and casings 204, 208 may be comprised of stainless steel that is treated with polytetrafluoroethylene (PTFE). It is contemplated that any of various PTFE-based formulations may be applied to the rod-ends 200, 224, without limitation. In some embodiments, PTFE-treated stainless steel balls and casings 204, 208 may be coupled with a lubricating race 228 that is comprised of an injection molded Teflon impregnated Nylon race, without limitation.

It is contemplated that the rod-ends 200, 224 may be treated during manufacturing so as to optimize hardness, strength, durability, and longevity. In some embodiments, the casings 208 may be machined 4130 chromoly, or any other suitable material, and the balls 204 may be comprised of 52100 bearing steel, or any other suitable material. The balls and casings 204, 208 may be heat-treated and hard-chrome finished so as to improve strength and corrosion resistance. Further, the balls and casings 204, 208, as well as the race 228, may be cryogenically treated to improve hardness, durability, and wear resistance.

While the invention has been described in terms of particular variations and illustrative figures, those of ordinary skill in the art will recognize that the invention is not limited to the variations or figures described. In addition, where methods and steps described above indicate certain events occurring in certain order, those of ordinary skill in the art will recognize that the ordering of certain steps may be modified and that such modifications are in accordance with the variations of the invention. Additionally, certain of the steps may be performed concurrently in a parallel process when possible, as well as performed sequentially as described above. To the extent there are variations of the invention, which are within the spirit of the disclosure or equivalent to the inventions found in the claims, it is the intent that this patent will cover those variations as well. Therefore, the present disclosure is to be understood as not limited by the specific embodiments described herein, but only by scope of the appended claims. 

What is claimed is:
 1. A leading-edge steering system for a front suspension of an off-road vehicle, comprising: a spindle assembly configured to support a drive axle assembly to conduct torque from a transaxle to a front wheel; a first rod-end joint configured to pivotally couple an upper suspension arm and the spindle assembly; a second rod-end joint configured to pivotally couple a lower suspension arm and the spindle assembly; a steering rod-end joint configured to pivotally couple a first end of a steering rod with a leading-edge portion of the spindle assembly; and a steering gear disposed in a chassis of the off-road vehicle and coupled with a second end of the steering rod.
 2. The steering system of claim 1, wherein the leading-edge portion of the spindle assembly is comprised of two parallel prongs extending forward with respect to the drive axle, the parallel prongs being configured to fixedly receive a bolt that hingedly receives the steering rod-end joint, such that moving the steering rod rotates the spindle assembly with respect to the upper suspension arm and the lower suspension arm.
 3. The steering system of claim 1, wherein the steering rod-end joint is comprised of a bushing that couples the steering rod with the spindle assembly, such that moving the steering rod rotates the spindle assembly with respect to the upper suspension arm and the lower suspension arm.
 4. The steering system of claim 3, wherein the bushing is configured to hingedly couple the steering rod with a bolt that is fastened through two parallel prongs extending forwardly from the spindle assembly.
 5. The steering system of claim 4, wherein the bushing is configured to facilitate horizontal rotation of the spindle assembly with respect to the upper suspension arm and the lower suspension arm during vertical motion of the spindle assembly during operation of the off-road vehicle.
 6. The steering system of claim 1, wherein the steering rod-end joint is comprised of a ball that is rotatable within a casing that is threadably coupled with the steering rod, such that moving the steering rod rotates the spindle assembly with respect to the upper suspension arm and the lower suspension arm.
 7. The steering system of claim 6, wherein the ball is configured to be fastened by way of a bolt between a pair of parallel prong extending forwardly from the spindle assembly, such that moving the steering rod rotates the spindle assembly horizontally with respect to the upper suspension arm and the lower suspension arm during vertical motion of the spindle assembly due to operation of the off-road vehicle.
 8. The steering system of claim 6, wherein the steering rod-end joint is coupled with the spindle assembly forward of the drive axle so as to advantageously decrease leverage of the front wheel on the steering rod and substantially eliminate bump steer that may occur due to traveling over rough terrain.
 9. The steering system of claim 1, wherein the steering gear is configured to move the steering rod rightward during clockwise turning of the steering gear, and wherein the steering gear is configured to move the steering rod leftward during counterclockwise turning of the steering gear.
 10. The steering system of claim 9, wherein the leading-edge portion is configured to rotate the spindle assembly rightward during clockwise turning of the steering gear, and wherein the leading-edge portion is configured to rotate the spindle assembly leftward during counterclockwise turning of the steering gear.
 11. The steering system of claim 1, wherein the leading-edge portion is configured to exert primarily tensile forces on the steering rod during traveling of the front wheel over rough terrain.
 12. The steering system of claim 11, wherein the leading-edge portion is configured to substantially eliminate bump steer that may occur due to forces exerted on the front wheel by the rough terrain. 